WO2003018990A2 - Systeme d'injection de carburant pour moteur a combustion interne - Google Patents

Systeme d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
WO2003018990A2
WO2003018990A2 PCT/DE2002/003139 DE0203139W WO03018990A2 WO 2003018990 A2 WO2003018990 A2 WO 2003018990A2 DE 0203139 W DE0203139 W DE 0203139W WO 03018990 A2 WO03018990 A2 WO 03018990A2
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
injection valve
valve member
injection
fuel
Prior art date
Application number
PCT/DE2002/003139
Other languages
German (de)
English (en)
Other versions
WO2003018990A3 (fr
Inventor
Joachim Winter
Gerhard Mack
Christoph Buehler
Friedrich Moser
Thomas Kuegler
Philippe Allio
Peter Boehland
Detlev Potz
Original Assignee
Robert Bosch Gmbh
SANDER-POTZ, Maike
Potz, Wendelin
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh, SANDER-POTZ, Maike, Potz, Wendelin filed Critical Robert Bosch Gmbh
Priority to KR10-2003-7005667A priority Critical patent/KR20040028662A/ko
Priority to EP02758167A priority patent/EP1423598A2/fr
Priority to JP2003523818A priority patent/JP2005500467A/ja
Priority to US10/415,082 priority patent/US6889658B2/en
Priority to BR0205939-8A priority patent/BR0205939A/pt
Publication of WO2003018990A2 publication Critical patent/WO2003018990A2/fr
Publication of WO2003018990A3 publication Critical patent/WO2003018990A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

  • the invention is based on one
  • Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from EP 0 957 261 AI. This
  • Fuel injection device has a high-pressure fuel pump and a fuel injection valve connected to each cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston which is driven by the internal combustion engine in a stroke movement and which delimits a pump work space which is connected to a pressure space of the fuel injection valve.
  • the fuel injection valve has an injection valve member, through which at least one injection opening is controlled and which can be moved in an opening direction against the closing force by the pressure prevailing in the pressure chamber. A connection of the is controlled by an electrically controlled control valve to control the fuel injection
  • the fuel injection device according to the invention with the features according to claim 1 has the advantage that additional injection cross section can be released or closed by the second injection valve member depending on the operating parameters of the internal combustion engine with the at least one second injection opening, so that the injection cross section to the
  • the injection cross section is controlled in a simple manner by the pressure generated by the feed pump as a function of the operating parameters in the control chamber.
  • an increased pressure in the control chamber is required for the blocking of the second injection valve member, which usually takes place at low load and / or speed of the internal combustion engine, and none at high load and / or speed increased pressure in the control chamber is required, so that an overload of the high-pressure fuel pump and the feed pump is counteracted because of the low pressure to be generated by the feed pump.
  • Fuel injection device for an internal combustion engine in a schematic representation according to a first
  • FIG. 2 shows an enlarged section of a section of FIG
  • FIG. 4 the section of the fuel injector denoted by II in FIG.
  • Fuel injector over time.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is designed as a so-called pump-nozzle system or as a pump-line-nozzle system and has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to each cylinder of the internal combustion engine.
  • the high-pressure fuel pump 10 is removed from the Fuel injection valve 12 arranged and connected to it via a line.
  • the fuel injection device is designed as a pump-nozzle system, with the high-pressure fuel pump 10 and the like
  • Fuel injection valve 12 are connected directly to one another and form a structural unit.
  • the high-pressure fuel pump 10 has a pump piston 18 which is tightly guided in a cylinder bore 16 in a pump body 14 and is driven in a lifting movement by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19.
  • the pump piston 18 delimits a pump working chamber 22 in the cylinder 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • the pump working chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle in a manner not shown.
  • the fuel injection valve 12 has a valve body 26, which can be constructed in several parts, in which a first injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
  • the valve body 26 has at least one first, preferably a plurality of first injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine, which are arranged distributed over the circumference of the valve body 26.
  • the first injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the first injection openings 32 lead away.
  • An annular space 38 is present in the valve body 26 between the injection valve member 28 and the bore 30 towards the valve seat 36 its end region facing away from the valve seat 36 merges into a pressure chamber 40 surrounding the first injection valve member 28 by a radial expansion of the bore 30.
  • the first injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 by reducing the cross section.
  • a first prestressed closing spring 44 engages, by means of which the first injection valve member 28 is pressed toward the valve seat 36.
  • the first closing spring 44 is arranged in a first spring chamber 46 of the valve body 26, which adjoins the bore 30.
  • Fuel injection valve 12 is hollow and a second injection valve member 128 is slidably guided therein in a bore formed coaxially in injection valve member 28.
  • the second injection valve member 128 controls at least one second injection opening 132 in the valve body 26.
  • the at least one second injection opening 132 is offset in the direction of the longitudinal axis of the injection valve members 28, 128 to the at least one first injection opening 32 toward the combustion chamber.
  • the second injection valve member 128 has, for example, an approximately conical sealing surface 134 on its end region facing the combustion chamber, which cooperates with a valve seat 136 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the second injection openings 132 lead away.
  • the second injection valve member 128 can be formed in two parts and have a part which has the sealing surface 134 and faces the combustion chamber and a second part which adjoins the first part away from the combustion chamber. Near the end of the second injection valve member 128 on the combustion chamber side there is a pressure surface 142 formed, on the pressure prevailing in the pressure chamber 40 when the first injection valve member 28 is open.
  • a second spring chamber 146 is formed in the valve body 26, in which a second closing spring 144 acting on the second injection valve member 128 is arranged.
  • the diameter of the second spring chamber 146 is somewhat smaller than that of the first spring chamber 46.
  • the end of the first injection valve member 28 projects into the first spring chamber 46 and is supported on the first closing spring 144.
  • the first closing spring 44 is supported with its end facing away from the first injection valve member 28 on a sleeve 47 arranged between the first spring chamber 46 and the second spring chamber 146.
  • the sleeve 47 is in turn supported on an annular shoulder formed at the transition from the first spring chamber 46 to the second spring chamber 146 by the reduction in diameter.
  • the sleeve 47 can be pressed into the first spring chamber 46 and thus fixed, or alternatively can be displaceable in the first spring chamber 46 in the direction of the longitudinal axis of the first injection valve member 28.
  • the second injection valve member 128 projects through the sleeve 47 into the second spring chamber 146 and is supported on the second closing spring 144 via a spring plate 147.
  • the second closing spring 144 is supported with its end facing away from the second valve member 128 at the bottom of the second spring chamber 146.
  • a control chamber 50 is delimited between the first spring chamber 46 and the second spring chamber 146 by the sleeve 47 on the one hand and the spring plate 147 on the other hand.
  • a channel 48 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 into the pressure chamber 40 of the fuel injection valve 12.
  • An electrically controlled valve 23 connects the Pump work chamber 22 controlled with a relief chamber, which can serve, for example, at least indirectly, the fuel reservoir 24 or an area in which a slightly higher pressure than the fuel reservoir 24 is maintained. As long as no fuel injection is to take place, the connection of the pump work chamber 22 to the relief chamber is opened by the control valve 23 controlled by an electronic control device 54, so that in the
  • control valve 23 separates the pump work chamber 22 from the relief chamber, so that high pressure can build up in the pump work chamber 22 during the delivery stroke of the pump piston 18.
  • the control valve 23 can be designed as a solenoid valve or as a piezo valve.
  • the fuel injection device is shown in Figures 1 to 3 according to a first embodiment.
  • the control chamber 50 is connected to a pressure source, for example in the form of a feed pump 52, which sucks fuel from the fuel reservoir 24.
  • the delivery pressure generated by the delivery pump 52 is controlled as a function of operating parameters of the internal combustion engine, such as, in particular, load, speed, temperature and, if appropriate, further parameters. It can be provided that the operation of the feed pump 52, in particular its speed, is controlled by a control device 54 as a function of the operating parameters. It can also be provided that a pressure relief valve 56 is provided in the connection between the control chamber 50 and the feed pump 52, which is controlled by the control device 54 and limits the feed pressure generated by the feed pump 52 to a predetermined value.
  • a channel 58 which opens into the control chamber 50 and via which the control chamber 50 is connected to the feed pump 52, is formed in the valve body 26. It can be provided that the channel 58 continues to the control valve 23 and that through the feed pump 52 via the channel 58 also fuel in the pump working chamber 22 during the suction stroke of the pump piston 18 and with the control valve 23 open.
  • the channel 58 and the pressure side of the feed pump 52 also serve as a relief chamber to which the pump working chamber 22 can be connected by the control valve 23 for controlling the fuel injection.
  • only one feed pump 52 is provided for the fuel injection devices of all cylinders of the internal combustion engine.
  • the second closing spring 144 presses the second injection valve member 128 with its sealing surface 134 against the second valve seat 136 in the valve body 26. Due to the pressure prevailing in the control chamber 50, a force which counteracts the force of the closing spring 144 is generated on the second injection valve member 128 via the spring plate 147.
  • the second closing spring 144 has a strong pretension so that it can hold the second injection valve member 128 in its closed position even when the pressure in the pressure chamber 40 of the fuel injection valve 12 is high, when the pressure in the control chamber 50 is low, and only open the second injection valve member 128 can, if there is an increased pressure in the control room 50.
  • the sleeve 47 is fixed in the first spring chamber 46, the pressure prevailing in the control chamber 50 has no effect on the first injection valve member 28. However, if the sleeve 47 is displaceable, the prestressing of the first closing spring 44 is increased with increasing pressure in the control chamber 50 via the then displaced sleeve 47, which forms a support for the first closing spring 44, and thus the opening pressure of the first injection valve member 28 is increased.
  • Fuel injector according to the first Exemplary embodiment explained.
  • the control valve 23 is opened, so that fuel reaches the pump working chamber 22 from the fuel reservoir 24.
  • the start of the fuel injection is determined by the control valve 23 closing, so that the pump work chamber 22 is separated from the relief chamber and high pressure builds up in the pump work chamber 22.
  • the pressure generated by the feed pump 52 and prevailing in the control chamber 50 is set. If a low pressure is generated in the control chamber 50 by the feed pump 52, the second injection valve member 128 is pressed by the second closing spring 144 with high force with its sealing surface 134 against the valve seat 136.
  • the fuel injection valve 12 opens by the the first injection valve member 28 lifts with its sealing surface 34 from the valve seat 36 and the at least one first injection opening 32 opens.
  • the closing force exerted on the second injection valve member 128 by the second closing spring 144 is greater than the force exerted on the second injection valve member 128 by the pressure prevailing in the pressure chamber 40, so that the second injection valve member 128 remains in its closed position.
  • only a part of the entire injection cross section is thus opened with the first injection openings 32, so that only a small amount of fuel is injected accordingly.
  • the feed pump 52 in the control chamber 50 switches on generates increased pressure, which acts on the second injection valve member 128 via the spring plate 147 and which supports the force generated in the pressure chamber 40 via the pressure surface 142 on the second injection valve member 128 in the opening direction 29. If the pressure in the control chamber 50, which is generated by the feed pump 52, and the pressure in the pressure chamber 40, which is generated by the pump piston 18, are high enough, in addition to the first injection valve member 28, the second injection valve member 128 also opens and gives the second Injection ports 132 free. Thus, the entire fuel injector 12
  • the end of the fuel injection is determined by the opening of the control valve 23, as a result of which the pump work chamber 22 is connected to the relief chamber and no high pressure can build up in it.
  • the injection cross sections formed by the first injection openings 32 and the second injection openings 132 are at least approximately the same size, so that when only the first injection valve member 28 is opened, half of the total
  • Injection cross section is released.
  • the first injection openings 32 form a larger or smaller injection cross section than the second injection openings 132.
  • Fuel injection in the control chamber 50 is set to a low pressure, so that with a small delivery stroke of the pump piston 18 only the first injection valve member 28 opens and only a part of the fuel injection valve 12 of the entire injection cross section is released. A small quantity of fuel is then pre-injected only through the first injection openings 32, which is designated by an injection phase I in FIG. As the delivery stroke of the pump piston 18 increases, an increased pressure can be set in the control chamber 50, so that the second injection valve member 128 also opens and the entire injection cross section is released on the fuel injection valve 12. There is then a main injection of a large amount of fuel through the first injection openings 32 and the second injection openings 132, which is designated in FIG. 5 with an injection phase II. Alternatively or additionally, it can be provided that at the beginning of a main fuel injection the pressure in the control chamber 50 is set such that only the first one
  • Injection valve member 28 opens and opens at least one first injection opening 32, and that the pressure in control chamber 50 is only set later during the main fuel injection in such a way that second injection valve member 128 also opens and opens at least one second injection opening 132.
  • a stepped main fuel injection is achieved for the injection phase II, as shown in FIG. 5, in which a small amount of fuel per unit time is initially injected through the first injection openings 32 and only later during the main fuel injection, a large amount of fuel per unit time through the first and second injection openings 32, 132 is injected.
  • the point in time at which the second injection openings 132 are opened is determined by the pressure in the control chamber 50.
  • the second injection valve member 128 Acting second closing spring 144 causes the second injection valve member 128 to open only a little later than the first injection valve member 28, as shown in Figure 5 with a solid line for the injection phase II, but due to the pressure prevailing in the control chamber 50, the time of opening of the second injection valve member 128 can be varied. Furthermore, it can also be provided that for certain operating parameters of the internal combustion engine, in particular at low load and / or speed, if only a small amount of fuel is injected, only the first injection valve member 28 opens and the second injection valve member 128 remains closed over the entire delivery stroke of the pump piston 18 ,
  • the closing force acting on the first injection valve member 28 increases with increasing pressure in the control chamber 50. If, as stated above, the pressure in the control chamber 50 is increased with increasing delivery stroke of the pump piston 18 and with increasing load and / or speed of the internal combustion engine, the opening pressure of the first injection valve member 28 also increases, that is the pressure in the pressure chamber 40 at which the first injection valve member 28 opens. A change in the opening pressure of the first injection valve member 28 as a function of operating parameters of the internal combustion engine is thus made possible without additional effort.
  • FIG. 4 shows a section of the fuel injection device according to a second exemplary embodiment, in which the basic structure is the same as in the first exemplary embodiment.
  • the control chamber is through the second spring chamber 246 formed and limited by the spring plate 147 formed as a piston of the second injection valve member 128.
  • the sleeve 47 is fixed in the first spring chamber 46 and is not acted upon by the pressure prevailing in the control chamber 246.
  • the pressure prevailing in the control chamber 246 acts on the second injection valve member 128 via the spring plate 147 and supports the force of the second closing spring 144.
  • the channel 58 formed in the valve body 26 and connected to the feed pump 52 opens into the control chamber 246.
  • the second injection valve member 128 has a low closing force, which is essentially generated by the pretensioning of the second closing spring 144. If there is an increased pressure in the control chamber 246, an increased closing force acts on the second injection valve member 128.
  • the function of the fuel injection device according to the second exemplary embodiment is essentially the same as in the first exemplary embodiment, but depending on operating parameters of the internal combustion engine, in particular at low load and / or speed, the delivery pump 52 in the control chamber 246 sets an increased pressure if only the first one Open injection valve member 28 and the second injection valve member 128 is to remain closed and only part of the entire injection cross section is to be released. Accordingly it becomes dependent on
  • a low pressure is set by the feed pump 52 in the control chamber 246 when the first injection valve member 28 and the second injection valve member 128 are to open and the entire injection cross section is to be released.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La présente invention concerne un système d'injection de carburant présentant pour chaque cylindre du moteur à combustion interne, une pompe à carburant haute pression (10) comprenant une chambre de pompe (22) et une soupape d'injection de carburant (12) reliée à celle-ci. La soupape d'injection de carburant (12) présente un premier élément de soupape d'injection (28) par lequel est commandée au moins une première ouverture d'injection (32), et qui peut être actionné par la pression produite dans la chambre de pompage (22) qui s'exerce dans une direction d'ouverture (29) contre une force de fermeture. Dans le premier élément de soupape d'injection (28) de forme creuse est guidé un second élément de soupape d'injection (128) par lequel est commandée au moins une seconde ouverture d'injection (132), et qui peut être actionné par la pression régnant dans la chambre de compression (40) qui s'exerce dans une direction d'ouverture (29) contre une force de fermeture, le second élément d'injection (128) subissant au moins indirectement l'effet de la pression régnant dans une chambre de commande (50) remplie de carburant, ladite pression étant produite par une pompe d'acheminement (52) en fonction de paramètres de fonctionnement du moteur à combustion interne, de sorte que le second élément de soupape d'injection (128) peut soit rester dans sa position fermée ou s'ouvrir.
PCT/DE2002/003139 2001-08-25 2002-08-23 Systeme d'injection de carburant pour moteur a combustion interne WO2003018990A2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR10-2003-7005667A KR20040028662A (ko) 2001-08-25 2002-08-23 엔진용 연료 분사 장치
EP02758167A EP1423598A2 (fr) 2001-08-25 2002-08-23 Systeme d'injection de carburant pour moteur a combustion interne
JP2003523818A JP2005500467A (ja) 2001-08-25 2002-08-23 内燃機関に用いられる燃料噴射装置
US10/415,082 US6889658B2 (en) 2001-08-25 2002-08-23 Fuel injection device for an internal combustion engine
BR0205939-8A BR0205939A (pt) 2001-08-25 2002-08-23 Dispositivo de injeção de combustìvel para um motor de combustão interna

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10141678A DE10141678A1 (de) 2001-08-25 2001-08-25 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10141678.4 2001-08-25

Publications (2)

Publication Number Publication Date
WO2003018990A2 true WO2003018990A2 (fr) 2003-03-06
WO2003018990A3 WO2003018990A3 (fr) 2003-08-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/003139 WO2003018990A2 (fr) 2001-08-25 2002-08-23 Systeme d'injection de carburant pour moteur a combustion interne

Country Status (10)

Country Link
US (1) US6889658B2 (fr)
EP (1) EP1423598A2 (fr)
JP (1) JP2005500467A (fr)
KR (1) KR20040028662A (fr)
CN (1) CN1466654A (fr)
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WO2004085825A1 (fr) * 2003-03-21 2004-10-07 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion interne

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DE10141678A1 (de) 2003-05-08
RU2003113561A (ru) 2005-01-20
JP2005500467A (ja) 2005-01-06
PL371271A1 (en) 2005-06-13
EP1423598A2 (fr) 2004-06-02
WO2003018990A3 (fr) 2003-08-14
KR20040028662A (ko) 2004-04-03
BR0205939A (pt) 2003-08-05
US20040065294A1 (en) 2004-04-08
US6889658B2 (en) 2005-05-10
CN1466654A (zh) 2004-01-07

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